Connect public, paid and private patent data with Google Patents Public Datasets

Centrufugal pump with thermally isolated and dynamically air cooled shaft seal assembly

Download PDF

Info

Publication number
US5624245A
US5624245A US08329172 US32917294A US5624245A US 5624245 A US5624245 A US 5624245A US 08329172 US08329172 US 08329172 US 32917294 A US32917294 A US 32917294A US 5624245 A US5624245 A US 5624245A
Authority
US
Grant status
Grant
Patent type
Prior art keywords
seal
pump
housing
shaft
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US08329172
Inventor
David M. DeClerck
Gregory S. Muller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MP Pumps Inc
Original Assignee
MP Pumps Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Grant date

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J15/00Sealings
    • F16J15/16Sealings between relatively-moving surfaces
    • F16J15/34Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/58Cooling; Heating; Diminishing heat transfer
    • F04D29/586Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5893Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps heat insulation or conduction
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05BINDEXING SCHEME RELATING TO MACHINES OR ENGINES OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, TO WIND MOTORS, TO NON-POSITIVE DISPLACEMENT PUMPS, AND TO GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY
    • F05B2240/00Components
    • F05B2240/60Shafts
    • F05B2240/61Shafts hollow

Abstract

A high temperature, centrifugal pump includes a thermally isolated and dynamically air cooled shaft seal. Carbon graphite insulators formed of plural elements juxtaposed together (46) insulate the seal assembly (34) from the pump housing (16). A hollow drive shaft limits heat conducted from the impeller during operation while a fan (56) forcibly flows air past the seal assembly to conduct heat energy away from the shaft seal. The insulator (46) reduces heat energy conducted to the seal assembly (42).

Description

BACKGROUND OF THE INVENTION

The present invention relates to a pump for pumping high temperature liquids, such as hot oil.

A typical centrifugal pump used for pumping hot liquids usually includes a volute type housing, an adapter, an impeller on a shaft, and a mechanical shaft seal. The mechanical seal must be capable of sealing the hot liquid and containing it within the pump. A disadvantage in such construction of pumps is that seal costs increase greatly when the pump has to be designed to handle liquid temperatures exceeding 400° F.

In the past, to achieve high temperature shaft sealing, expensive and elaborate seals with hard faces or water cooling of the seal cavity with remote heat exchangers have been used. These heat exchangers are expensive to operate because of the large amount of cooling water required. As a result of past experience, there is a need for a pump that is not water cooled, does not use elaborate seals, and which is capable of pumping high temperature liquid.

Prior art pumps, such as those shown in U.S. Pat. No. 4,720,248 and Great Britain Patent Document 728077 disclose attempts made at thermally protecting the motor of the pump but do not contemplate attempting to reduce the temperature of the seal housings or seals. The aforementioned prior art patents show pumps that do not adequately address the problem of insulation of hot liquid from mechanical seals nor of seal wear.

Additionally, some prior air pumps, such those shown in U.S. Pat. No. 4,979,875, utilize long distances from the pump to the seal to allow for adequate dissipation of heat. In some applications it would be preferable for the pump unit to be made as small as possible.

SUMMARY OF THE INVENTION

The present invention overcomes the disadvantages of the above-described prior art centrifugal pumps by providing a carbon graphite insulator between the seal housing and an adapter adjacent the pump liquid to thermally insulate the mechanical seal. Such construction allows the pump to withstand fluid temperatures over 400° F.

Generally, the invention in one form thereof, provides a pump having a common volute type pump housing for mounting and liquid pressure/velocity conversion. An impeller is disposed therein to transfer shaft energy from a motor into the liquid. A seal housing is provided for supporting and thermal isolation of a mechanical seal. The seal and housing is thermally isolated from the pump housing by means of carbon insulators and a hollow drive shaft.

More specifically, a carbon insulator is mounted between the seal housing and the pump housing to reduce transfer of heat energy into the seal housing. The insulator maintains the temperature in the seal housing below that of the liquid that is being pumped. A hollow drive shaft further assists in thermally isolating the seal housing. A commercially available bellows type end face shaft seal is used in the seal housing and is located onto and driven by the drive shaft. The seal housing has internal and external cast fins to aid in cooling.

In one form of the invention, a fan clamped on the drive shaft provides positive mechanical engagement between the drive shaft and the motor while causing air to move across the seal housing via rotating fan blades thereby cooling the cavity with forced air convection.

An advantage of the pump of the present invention is that the seal cavity, including the mechanical seal, is cooled via a forced convection of air and thermally insulated from the pump liquid by the carbon graphite insulator thereby reducing heat transfer to the seal. With external air cooling, reduction of seal oil temperature as great as 370° F. below pumpage temperature is possible.

Another advantage of the pump of the present invention is that of reduced cost by use of a simple mechanical seal between the hot liquid and drive shaft.

A further advantage of the pump of the present invention is that pump down time is reduced since oxidation and coking of the seal is reduced by the minimized seal operating temperature. Initial and operating costs are reduced as compared to a pump having high temperature, elaborate seals and other cooling devices. An additional backup lip seal reduces oxidation of the mechanical seal by limiting the amount air able to reach the mechanical seal.

Yet another advantage of the pump of the present invention is that of a close coupled design that eliminates coupling misalignment and provides for compact integration within a heating system unit. The close coupling allows the rotating assembly to be removed without disturbing associated piping when routine maintenance must be performed. A byproduct of the close coupled design is that the pump unit is shorter in length that prior pumps, reducing the amount of space needed for the pump,

Another advantage of the pump of the present invention is that the seal cavity vents all entrapped gas on startup and no additional venting procedure is required.

The invention, in one form thereof, provides a high temperature liquid pump for attachment to a motor including a pump casing having an end wall and a pump housing. An impeller is rotatably disposed within the pump housing for pumping high temperature liquid. A drive shaft connects the motor to the impeller with the drive shaft passing through the end wall. A seal assembly including a seal housing having a mechanical seal is located about the drive shaft and connected to the pump housing. A carbon graphite insulator is disposed between the pump housing and seal housing to reduce heat transfer from the pump housing to the seal and seal housing.

In one form of the invention, the drive shaft is hollow between the impeller and seal whereby the seal housing is further insulated to reduce heat energy entering from the pump housing.

BRIEF DESCRIPTION OF THE DRAWINGS

The above-mentioned and other features and advantages of this invention, and the manner of attaining them, will become more apparent and the invention will be better understood by reference to the following description of an embodiment of the invention taken in conjunction with the accompanying drawings, wherein:

FIG. 1 is a longitudinal sectional view of a preferred embodiment of a pump of the type to which the present invention pertains;

FIG. 2 is an end elevational view of the pump of FIG. 1.

Corresponding reference characters indicate corresponding parts throughout the several views. The exemplification set out herein illustrates one preferred embodiment of the invention, in one form, and such exemplification is not to be construed as limiting the scope of the invention in any manner.

DETAILED DESCRIPTION OF THE INVENTION

In an exemplary embodiment of the invention as shown in the drawings and particularly referring to FIG. 1, a high temperature pump 10 includes a ductile iron pump adapter casing 12 having an endwall 14 and having a pump housing 16 attached to endwall 14 by a plurality of screws 18 with associated lock washers 20. Casing 12 includes four mounting brackets 21 formed on a rear surface opposite end wall 14 to which attaches a motor (not shown) to drive pump 10.

A cast iron impeller 22 is rotatably disposed within pump housing 16 for pumping high temperature liquid, such as hot oil, from a liquid inlet 24 and out through liquid outlet 26. Impeller 22 may be of the enclosed type as shown or a semi-open type as known in the art. A thin walled, stainless steel, sleeve-type drive shaft 28 connects from a motor (not shown) to impeller 22 through casing 12 and endwall 14. A jam nut 30 locks impeller 22 onto drive shaft 28.

A seal assembly 32 is utilized to mechanically seal drive shaft 28 to prevent leakage. Seal assembly 32 includes a ductile iron seal housing 34 disposed in air filled interior cavity 62 of casing 12 substantially separated and spaced apart by an air gap from both casing 12 and pump housing 16 for increased heat transmission away from the mechanical seal 42. The surfaces of seal housing 34 include a plurality of external fins 36 and internal fins 38 to efficiently radiate heat. A chamber 40 is formed in seal housing 34 about drive shaft 28 onto which is located a mechanical seal 42 which mechanically seals oil or liquid within chamber 40 from passing between seal housing 34 and drive shaft 28 to the area of fan 56. A plurality of bolts 44 attach seal housing 34 to endwall 14 of casing 12. A backup lip seal 50 of conventional construction is located on seal housing 34 about drive shaft 28. This seal 50 reduces oxidation of the mechanical seal 42 by limiting air flow past drive shaft 28.

Mechanical seal 42 is preferably a standard mechanical seal that requires no service adjustment. A preferred type of mechanical seal commercially available for use is a Type 2 seal from John Crane, Inc. of Morton Grove, Ill.

As shown in FIG. 1, carbon graphite insulators 46 are disposed between endwall 14 of casing 12 and seal housing 34. Preferably, carbon graphite insulators are of the type sold by Carbide Technology of Hartford, Conn., Grade No. CTI-87, although other insulators may be utilized. Insulators of low thermal conduction in the range of approximately 5 to 9 BTU/hr ft °F. may be used. In particular, the preferred CTI-87 insulator has a thermal conductivity of approximately 5 BTU/hr ft °F. Each insulator 46 includes an annular recess 47 on one side and a small annular protuberance 49 on an opposite side. The stacking of the two carbon graphite insulators 46 with a protuberance 49 of one interfitting into a recess 47 of another forms an annular air pocket 48 which assists in insulating against heat transfer. Stagnate air within air pocket 48 assists insulator 46 in reducing heat flow from pump housing 16 to seal housing 34. Other equivalent mechanisms for creating volumes of stagnate air in and between insulators 46 may be used.

As shown in FIG. 1, gaskets 52 may be located between sealing surfaces as between casing 12 and pump housing 16 and between carbon graphite insulators 46.

An annular passage 54, between drive shaft 28 and carbon graphite insulators 46, permits pumpage to flow between the intake area of pump housing 16 and reservoir 40. At initial pump startup, pumpage will pass from pump housing 16 through annular passage 54 into reservoir 40 to assist in lubricating mechanical seal 42. After reservoir 40 is filled, little liquid circulates through annular passageway 54.

To assist in cooling of pump 10 and specifically seal assembly 32, an external air cooling system is provided having a shaft driven fan 56 having fan blades 58. Fan 56 is formed in two halves about a plane through the axis of fan rotation. Fan 56 is directly clamped to drive shaft 28 by means of bolts 60 passing through and connecting each half of fan 56 about drive shaft 28. Fan 56 and bolts 60 together attach drive shaft 28 to the power output shaft of a motor (not shown) by causing the two halves of fan 56 to clamp both drive shaft 28 and output shaft therebetween. Bolts 60 are oriented transverse to the axis of fan rotation to connect the two halves of fan 56 together.

During operation, the output shaft of the motor will rotate drive shaft 28 connected by means of fan 56 and bolts 60. As drive shaft 28 rotates, impeller 22 will rotate within pump housing 16 causing high temperature oil or other liquids to be drawn into inlet 24 and slung outwardly and through liquid outlet 26. At initial startup a small quantity of hot liquid will flow through annular passage 54 into seal chamber 40 to lubricate mechanical seal 42. Cooling of pump 10, particularly the mechanical seal 42, is caused by the insulative effect of carbon graphite insulators 46, air pockets 48, along with the forced air cooling created by the rotation of fan 56. Heat energy is additionally withdrawn from reservoir 40 and mechanical seal 42 by internal fins 38 that conduct heat energy into the body of seal housing 34. Fan blades 58 of fan 56 will cause air to flow over blades 58 and past the exterior fins 36 of seal housing 34, thereby picking up heat and pulling it away from seal housing 34 and mechanical seal 42 into the interior 62 of casing 12. After picking up heat, air will then flow out of interior 62 through a plurality of air holes 64.

While this invention has been described as having a preferred design, the present invention can be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the invention using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains and which fall within the limits of the appended claims.

Claims (6)

What is claimed is:
1. A high temperature liquid pump comprising:
a pump housing having an end wall;
an impeller rotatably disposed in said pump housing;
a drive shaft connected to said impeller, said drive shaft passing through said end wall;
a seal housing enclosing a mechanical seal located about said drive shaft, said seal housing spaced apart from said pump housing; and
a thermal insulator disposed between said pump housing and said seal housing and spacing apart said housings to reduce heat transfer from said pump housing to said seal housing;
wherein said insulator is formed of plural elements axially juxtaposed to each other; and
wherein each said element includes a protuberance on one side and a recess on an opposite side, said protuberance of one element interfitting into the recess of an axially juxtaposed element.
2. The pump of claim 1 in which said recess located between said axial juxtaposed elements creates an air pocket to decrease heat flow therethrough.
3. The pump of claim 1 wherein said thermal insulator comprises a thermal conductivity of between about 5 and 9 BTU/hr ft °F.
4. The pump of claim 3 wherein said thermal insulator comprises a thermal conductivity of about 5 BTU/hr ft °F.
5. A high temperature liquid pump comprising:
a pump housing having an end wall;
an impeller rotatably disposed in said pump housing;
a drive shaft connected to said impeller, said drive shaft passing through said end wall;
a seal housing enclosing a mechanical seal located about said drive shaft;
a thermal insulator disposed between said pump housing and said seal housing and spacing apart said housings, wherein said insulator is formed of plural elements axially juxtaposed to each other, and wherein each said element includes a protuberance on one side and a recess on an opposite side, said protuberance of one element interfitting into the recess of an axially juxtaposed element; and
wherein said seal housing is supportably mounted to said insulator in spaced apart relationship with said pump housing to define a gap for cooling air, wherein said gap and said insulator between said pump housing and said seal housing reduces heat transfer from said pump housing to said seal housing.
6. The pump of claim 1 in which said recess located between said axial juxtaposed elements creates an air pocket to decrease heat flow therethrough.
US08329172 1994-10-26 1994-10-26 Centrufugal pump with thermally isolated and dynamically air cooled shaft seal assembly Expired - Lifetime US5624245A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US08329172 US5624245A (en) 1994-10-26 1994-10-26 Centrufugal pump with thermally isolated and dynamically air cooled shaft seal assembly

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US08329172 US5624245A (en) 1994-10-26 1994-10-26 Centrufugal pump with thermally isolated and dynamically air cooled shaft seal assembly

Publications (1)

Publication Number Publication Date
US5624245A true US5624245A (en) 1997-04-29

Family

ID=23284190

Family Applications (1)

Application Number Title Priority Date Filing Date
US08329172 Expired - Lifetime US5624245A (en) 1994-10-26 1994-10-26 Centrufugal pump with thermally isolated and dynamically air cooled shaft seal assembly

Country Status (1)

Country Link
US (1) US5624245A (en)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5911565A (en) * 1995-03-06 1999-06-15 Sterling Fluid Systems (Germany) Gmbh Pump for conveying hot media
WO1999065769A2 (en) * 1998-06-15 1999-12-23 Lockheed Martin Corporation Electrical drive system for rocket engine propellant pumps
US6227819B1 (en) 1999-03-29 2001-05-08 Walbro Corporation Fuel pumping assembly
US6231318B1 (en) 1999-03-29 2001-05-15 Walbro Corporation In-take fuel pump reservoir
US6273684B1 (en) * 1999-03-31 2001-08-14 Grundfos A/S Centrifugal pump unit
DE10013152A1 (en) * 2000-03-17 2001-09-20 Ksb Ag seal housing
US6634854B1 (en) * 1997-05-21 2003-10-21 Ksb Aktiengesellschaft Machinery unit with integrated heat barrier
US20030214099A1 (en) * 2002-05-20 2003-11-20 Dahlheimer John C. Fan cooled seal seat
WO2006001610A1 (en) * 2004-06-24 2006-01-05 Lg Electronics, Inc. Leakage preventing structure of dish washer
US20060177325A1 (en) * 2004-01-16 2006-08-10 Peterson David J Jr Motor-driven pump for pool or spa
US20070065317A1 (en) * 2005-09-19 2007-03-22 Ingersoll-Rand Company Air blower for a motor-driven compressor
US20070126605A1 (en) * 2003-08-16 2007-06-07 Daimlerchrysler Ag Method for updating a digital map
CN100413454C (en) 2005-06-29 2008-08-27 乐金电子(天津)电器有限公司 Water leak preventing structure of dish washer
US20100272560A1 (en) * 2009-04-28 2010-10-28 Buell Steven E Centrifugal Pump with Improved Drive Shaft and Heat Exchanger
US20110164997A1 (en) * 2008-09-08 2011-07-07 Siemens Aktiengesellschaft Pump
US20120076643A1 (en) * 2009-06-04 2012-03-29 Ksb Aktiengesellschaft Sealing System for Centrifugal Pumps
US8333666B2 (en) 2004-12-10 2012-12-18 Sundyne Corporation Inner drive for magnetic drive pump
US20150308288A1 (en) * 2014-04-23 2015-10-29 Sikorsky Aircraft Corporation Impeller retention apparatus

Citations (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1400323A (en) * 1918-08-01 1921-12-13 Earl H Sherbondy Turbo-compressor casing
US1611547A (en) * 1925-01-31 1926-12-21 Allen O Miller Hub for fan blowers
US2203525A (en) * 1936-08-04 1940-06-04 Jr Samuel F Dupree Sealing means for shafts
US2239228A (en) * 1938-01-21 1941-04-22 Lewis E Hankison Pump mechanism
US2423825A (en) * 1945-07-06 1947-07-15 Byron Jackson Co Motor pump unit
GB728077A (en) * 1952-08-14 1955-04-13 Sigmund Pumps Ltd Combined pump and driving motor assembly
US3056354A (en) * 1960-01-26 1962-10-02 George A Gerard Impeller pump
US3076412A (en) * 1959-03-04 1963-02-05 Bell & Gossett Co Method and apparatus for maintaining rotating pump seals
US3088416A (en) * 1961-07-21 1963-05-07 Gen Fittings Company Centrifugal pump
US3089423A (en) * 1960-11-25 1963-05-14 Union Carbide Corp Corrosive resistant pump
GB965939A (en) * 1962-01-22 1964-08-06 Sigmund Pumps Ltd Air cooling of close-coupled pump and motor units
US3217656A (en) * 1963-10-02 1965-11-16 Borg Warner Air cooled bearing housing
US3467014A (en) * 1967-05-11 1969-09-16 Itt Close-coupled booster pump
US3478689A (en) * 1967-08-02 1969-11-18 Borg Warner Circulating pump
US3500754A (en) * 1968-01-25 1970-03-17 Loewe Pumpenfabrik Gmbh Centrifugal pump units
US3554661A (en) * 1968-12-20 1971-01-12 Decatur Pump Co High temperature pump
US3600101A (en) * 1969-12-22 1971-08-17 Decatur Pump Co Compact high temperature pump
US3630529A (en) * 1969-05-05 1971-12-28 Borg Warner Sodium vapor trap
US3914072A (en) * 1974-11-19 1975-10-21 Weil Mclain Company Inc Fluid pumping assembly
US3941395A (en) * 1973-03-08 1976-03-02 Borg-Warner Corporation Cooled seal cartridge
US3947154A (en) * 1973-06-19 1976-03-30 Klein, Schanzlin & Becker Aktiengesellschaft Pump assembly for circulation of coolant in boiling water reactors or the like
US4109920A (en) * 1977-09-06 1978-08-29 Borg-Warner Corporation Heat exchanger for shaft seal cartridge
US4114899A (en) * 1974-02-22 1978-09-19 Friedhelm Kulzer Cooled mechanical seal
US4239462A (en) * 1977-03-10 1980-12-16 Klein, Schanzlin & Becker Aktiengesellschaft Heat barrier for motor-pump aggregates
US4720248A (en) * 1980-04-30 1988-01-19 Klein, Schanzlin & Becker Aktiengesellschaft Thermal barrier for submersible pump and motor assemblies
US4979875A (en) * 1986-10-17 1990-12-25 Sihi Gmbh & Co. Kg Centrifugal pump for the delivery of hot liquids
US5051071A (en) * 1990-02-09 1991-09-24 Haentjens Walter D Heat dissipating coupling for rotary shafts
US5195867A (en) * 1992-03-05 1993-03-23 Barrett, Haentjens & Co. Slurry pump shaft seal flushing

Patent Citations (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1400323A (en) * 1918-08-01 1921-12-13 Earl H Sherbondy Turbo-compressor casing
US1611547A (en) * 1925-01-31 1926-12-21 Allen O Miller Hub for fan blowers
US2203525A (en) * 1936-08-04 1940-06-04 Jr Samuel F Dupree Sealing means for shafts
US2239228A (en) * 1938-01-21 1941-04-22 Lewis E Hankison Pump mechanism
US2423825A (en) * 1945-07-06 1947-07-15 Byron Jackson Co Motor pump unit
GB728077A (en) * 1952-08-14 1955-04-13 Sigmund Pumps Ltd Combined pump and driving motor assembly
US3076412A (en) * 1959-03-04 1963-02-05 Bell & Gossett Co Method and apparatus for maintaining rotating pump seals
US3056354A (en) * 1960-01-26 1962-10-02 George A Gerard Impeller pump
US3089423A (en) * 1960-11-25 1963-05-14 Union Carbide Corp Corrosive resistant pump
US3088416A (en) * 1961-07-21 1963-05-07 Gen Fittings Company Centrifugal pump
GB965939A (en) * 1962-01-22 1964-08-06 Sigmund Pumps Ltd Air cooling of close-coupled pump and motor units
US3217656A (en) * 1963-10-02 1965-11-16 Borg Warner Air cooled bearing housing
US3467014A (en) * 1967-05-11 1969-09-16 Itt Close-coupled booster pump
US3478689A (en) * 1967-08-02 1969-11-18 Borg Warner Circulating pump
US3500754A (en) * 1968-01-25 1970-03-17 Loewe Pumpenfabrik Gmbh Centrifugal pump units
US3554661A (en) * 1968-12-20 1971-01-12 Decatur Pump Co High temperature pump
US3630529A (en) * 1969-05-05 1971-12-28 Borg Warner Sodium vapor trap
US3600101A (en) * 1969-12-22 1971-08-17 Decatur Pump Co Compact high temperature pump
US3941395A (en) * 1973-03-08 1976-03-02 Borg-Warner Corporation Cooled seal cartridge
US3947154A (en) * 1973-06-19 1976-03-30 Klein, Schanzlin & Becker Aktiengesellschaft Pump assembly for circulation of coolant in boiling water reactors or the like
US4114899A (en) * 1974-02-22 1978-09-19 Friedhelm Kulzer Cooled mechanical seal
US3914072A (en) * 1974-11-19 1975-10-21 Weil Mclain Company Inc Fluid pumping assembly
US4239462A (en) * 1977-03-10 1980-12-16 Klein, Schanzlin & Becker Aktiengesellschaft Heat barrier for motor-pump aggregates
US4109920A (en) * 1977-09-06 1978-08-29 Borg-Warner Corporation Heat exchanger for shaft seal cartridge
US4720248A (en) * 1980-04-30 1988-01-19 Klein, Schanzlin & Becker Aktiengesellschaft Thermal barrier for submersible pump and motor assemblies
US4979875A (en) * 1986-10-17 1990-12-25 Sihi Gmbh & Co. Kg Centrifugal pump for the delivery of hot liquids
US5051071A (en) * 1990-02-09 1991-09-24 Haentjens Walter D Heat dissipating coupling for rotary shafts
US5195867A (en) * 1992-03-05 1993-03-23 Barrett, Haentjens & Co. Slurry pump shaft seal flushing

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5911565A (en) * 1995-03-06 1999-06-15 Sterling Fluid Systems (Germany) Gmbh Pump for conveying hot media
US6634854B1 (en) * 1997-05-21 2003-10-21 Ksb Aktiengesellschaft Machinery unit with integrated heat barrier
WO1999065769A2 (en) * 1998-06-15 1999-12-23 Lockheed Martin Corporation Electrical drive system for rocket engine propellant pumps
WO1999065769A3 (en) * 1998-06-15 2000-03-23 Lockheed Corp Electrical drive system for rocket engine propellant pumps
US6231318B1 (en) 1999-03-29 2001-05-15 Walbro Corporation In-take fuel pump reservoir
US6227819B1 (en) 1999-03-29 2001-05-08 Walbro Corporation Fuel pumping assembly
US6273684B1 (en) * 1999-03-31 2001-08-14 Grundfos A/S Centrifugal pump unit
DE10013152A1 (en) * 2000-03-17 2001-09-20 Ksb Ag seal housing
EP1134424A3 (en) * 2000-03-17 2002-10-09 KSB Aktiengesellschaft A seal housing
US7108266B2 (en) * 2002-05-20 2006-09-19 Freudenberg-Nok General Partnership Fan cooled seal seat
US20030214099A1 (en) * 2002-05-20 2003-11-20 Dahlheimer John C. Fan cooled seal seat
US20070126605A1 (en) * 2003-08-16 2007-06-07 Daimlerchrysler Ag Method for updating a digital map
US20060177325A1 (en) * 2004-01-16 2006-08-10 Peterson David J Jr Motor-driven pump for pool or spa
US20090100589A1 (en) * 2004-01-16 2009-04-23 Peterson Jr David J Motor-driven pump for pool or spa
WO2006001610A1 (en) * 2004-06-24 2006-01-05 Lg Electronics, Inc. Leakage preventing structure of dish washer
US7771543B2 (en) 2004-06-24 2010-08-10 Lg Electronics Inc. Leakage preventing structure of dish washer
US20080163903A1 (en) * 2004-06-24 2008-07-10 Jong-Chul Bang Leakage Preventing Structure of Dish Washer
US8333666B2 (en) 2004-12-10 2012-12-18 Sundyne Corporation Inner drive for magnetic drive pump
US9362050B2 (en) 2004-12-10 2016-06-07 Sundyne, Llc Inner drive for magnetic drive pump
CN100413454C (en) 2005-06-29 2008-08-27 乐金电子(天津)电器有限公司 Water leak preventing structure of dish washer
US9261104B2 (en) 2005-09-19 2016-02-16 Ingersoll-Rand Company Air blower for a motor-driven compressor
US20070065317A1 (en) * 2005-09-19 2007-03-22 Ingersoll-Rand Company Air blower for a motor-driven compressor
US20110164997A1 (en) * 2008-09-08 2011-07-07 Siemens Aktiengesellschaft Pump
US8152458B2 (en) * 2009-04-28 2012-04-10 Mp Pumps, Inc. Centrifugal pump with improved drive shaft and heat exchanger
US20100272560A1 (en) * 2009-04-28 2010-10-28 Buell Steven E Centrifugal Pump with Improved Drive Shaft and Heat Exchanger
US8870521B2 (en) * 2009-06-04 2014-10-28 Ksb Aktiengesellschaft Sealing system for centrifugal pumps
US20120076643A1 (en) * 2009-06-04 2012-03-29 Ksb Aktiengesellschaft Sealing System for Centrifugal Pumps
CN102803737B (en) * 2009-06-04 2016-03-16 Ksb 股份公司 Centrifugal sealing system
CN102803737A (en) * 2009-06-04 2012-11-28 Ksb 股份公司 Sealing system for centrifugal pumps
US20150308288A1 (en) * 2014-04-23 2015-10-29 Sikorsky Aircraft Corporation Impeller retention apparatus
US9567871B2 (en) * 2014-04-23 2017-02-14 Sikorsky Aircraft Corporation Impeller retention apparatus

Similar Documents

Publication Publication Date Title
US3229130A (en) Motors having an air-gap jacket in particular for central heating accelerators and other like applications
US3347168A (en) Motor pump unit
US5269664A (en) Magnetically coupled centrifugal pump
US4725206A (en) Thermal isolation system for turbochargers and like machines
US4740711A (en) Pipeline built-in electric power generating set
US2763214A (en) Motor driven pumps
US2734459A (en) zimsky
US5954124A (en) Heat exchanging device
US6012909A (en) Centrifugal pump with an axial-field integral motor cooled by working fluid
US6379127B1 (en) Submersible motor with shaft seals
US5890880A (en) Sealed motor driven centrifugal fluid pump
US3192861A (en) High temperature canned motor pump
US5217234A (en) Mechanical seal with barrier fluid circulation system
US3916231A (en) Induction motor
US2824759A (en) Liquid cooled seal
US3554661A (en) High temperature pump
US5009578A (en) Motor driven pumps
US3263424A (en) Turbine-compressor unit
US4283167A (en) Cooling structure for an oil sealed rotary vacuum pump
US2891391A (en) Refrigerated hermetically sealed motors
US2913988A (en) Motor driven pumps
US3999376A (en) One-piece ceramic support housing for a gas turbine with a rotary regenerator
US3135211A (en) Motor and pump assembly
US6208512B1 (en) Contactless hermetic pump
US5332369A (en) Pump unit with cooling jacket for electric motor

Legal Events

Date Code Title Description
AS Assignment

Owner name: MP PUMPS, INC., MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:DECLERCK, DAVID M.;MULLER, GREGORY S.;REEL/FRAME:007233/0591

Effective date: 19941024

FPAY Fee payment

Year of fee payment: 4

FPAY Fee payment

Year of fee payment: 8

AS Assignment

Owner name: JPMORGAN CHASE BANK, N.A., MICHIGAN

Free format text: SECURITY AGREEMENT;ASSIGNOR:TECUMSEH PRODUCTS COMPANY;REEL/FRAME:016641/0380

Effective date: 20050930

Owner name: JPMORGAN CHASE BANK, N.A.,MICHIGAN

Free format text: SECURITY AGREEMENT;ASSIGNOR:TECUMSEH PRODUCTS COMPANY;REEL/FRAME:016641/0380

Effective date: 20050930

AS Assignment

Owner name: CITICORP USA, INC., NEW YORK

Free format text: SECURITY INTEREST;ASSIGNORS:TECUMSEH PRODUCTS COMPANY;CONVERGENT TECHNOLOGIES INTERNATIONAL, INC.;TECUMSEH TRADING COMPANY;AND OTHERS;REEL/FRAME:017606/0644

Effective date: 20060206

Owner name: CITICORP USA, INC.,NEW YORK

Free format text: SECURITY INTEREST;ASSIGNORS:TECUMSEH PRODUCTS COMPANY;CONVERGENT TECHNOLOGIES INTERNATIONAL, INC.;TECUMSEH TRADING COMPANY;AND OTHERS;REEL/FRAME:017606/0644

Effective date: 20060206

AS Assignment

Owner name: JPMORGAN CHASE BANK, N.A., NEW YORK

Free format text: SECURITY AGREEMENT;ASSIGNORS:TECUMSEH PRODUCTS COMPANY;TECUMSEH COMPRESSOR COMPANY;VON WEISE USA, INC.;AND OTHERS;REEL/FRAME:020995/0940

Effective date: 20080320

Owner name: JPMORGAN CHASE BANK, N.A.,NEW YORK

Free format text: SECURITY AGREEMENT;ASSIGNORS:TECUMSEH PRODUCTS COMPANY;TECUMSEH COMPRESSOR COMPANY;VON WEISE USA, INC.;AND OTHERS;REEL/FRAME:020995/0940

Effective date: 20080320

AS Assignment

Owner name: FIRSTRUST BANK, PENNSYLVANIA

Free format text: SECURITY AGREEMENT;ASSIGNOR:M.P. PUMPS, INC., A MICHIGAN CORPORATION;REEL/FRAME:021230/0144

Effective date: 20080630

AS Assignment

Owner name: SPRING CAPITAL PARTNERS II L.P., PENNSYLVANIA

Free format text: SECURITY AGREEMENT;ASSIGNORS:M.P. PUMPS INC.;MP PUMPS ACQUISITION CORPORATION;MPP FLUID TECHNOLOGY LLC;REEL/FRAME:021266/0490

Effective date: 20080630

FPAY Fee payment

Year of fee payment: 12

AS Assignment

Owner name: M. P. PUMPS, INC., MICHIGAN

Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:CITICORP USA, INC.;REEL/FRAME:036327/0380

Effective date: 20080430

Owner name: M. P. PUMPS, INC., MICHIGAN

Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:JP MORGAN CHASE BANK, N.A.;REEL/FRAME:036327/0292

Effective date: 20080428

AS Assignment

Owner name: JPMORGAN CHASE BANK, N.A., ILLINOIS

Free format text: SECURITY INTEREST;ASSIGNOR:M.P. PUMPS, INC.;REEL/FRAME:036419/0915

Effective date: 20150818

AS Assignment

Owner name: M.P. PUMPS, INC., MICHIGAN

Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:FIRSTTRUST BANK;REEL/FRAME:036609/0686

Effective date: 20150915

Owner name: M.P. PUMPS, INC., MICHIGAN

Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:FIRSTRUST BANK;REEL/FRAME:036609/0844

Effective date: 20150915

AS Assignment

Owner name: MP PUMPS, INC., MICHIGAN

Free format text: RELEASE BY SECURED PARTY;ASSIGNOR:JPMORGAN CHASE BANK, N.A.;REEL/FRAME:037303/0392

Effective date: 20151210